Change gear mechanism



April 14, 1954 D. N. OBENSHAIN 3,128,662

CHANGE GEAR MECHANISM Filed Jan. 13, 1961 4 Sheets-Sheet 1 FIG. 2.

Imllllllll lllllllllllllllll INVENTOR BY D. NOEL OBENSHAIN A ORNEYS.

Ap 1964 D. N. OBENSHAIN CHANGE GEAR MECHANISM Filed Jan. 13, 1961 IIIIIIIIIIIIIIIIIIIIIIIII% 5 4 Sheets-Sheet 2 INVENTOR D. NOEL OBENSHAIN M lRNEYS.

April 14, 1954 D. N. OBENSHAIN 3,128,662

CHANGE GEAR MECHANISM Filed Jan. 13, 1961 4 Sheets-Sheet 3 F IG. 6.

FIG. 5.

o 0 j I\ 0 -5 0 .2 I78 INV'ENTOR D. NOEL OBENSHAlN BY 612.0 5-

ATTORNEYS.

United States Patent 3,128,662 CHANGE GEAR MECHANHSM David Noel Uhenshain, Luise, M11, assignor to West Virginia Pulp and Paper Company, New York, N.Y., a corporation of Delaware Filed Jan. 13, 1961, Ser. No. 82,487 4 Claims. (Cl. 81-298) This invention relates to change gear mechanism. While the novel mechanism is capable of many uses, it has been especially contrived for use in paper cutting machinery and will therefore be illustratively disclosed in connection with that use.

In a paper cutting machine it is desirable and important;

(1) That the length of the web fed in a cutter cycle be precisely predetermined and positively controlled, so that there will be no lack of uniformity of sheet length and no need for following the wasteful practice of subsequently edge trimming the paper;

(2) That the machine be quickly and conveniently settable to feed consistently any one of a multiplicity of predetermined web lengths per cutter cycle, which lengths differ but slightly from one another and form collectively an unbroken arithmetical series between Widely spaced lower and upper limits;

(3) That a change gear unit be provided for controlling the web length setting (a) which can be easily understood and set, even by an untrained operator; (b) which is positive in its action; (0) which is rugged and dependable in use; and (d) which is constructed and arranged in a simple, compact and orderly manner so that it involves relatively little material cost, but more particularly so that it involves little inital labor cost in the assembly of its parts and can be disassembled and reassembled economically and quickly when servicing is required.

The present invention is characterized by the fact that all of the above stated desiderata are realized.

Other objects and advantages will hereinafter appear.

In the drawing forming part of this specification FIG. 1 is a fragmentary diagrammatic view in side elevation showing the disposition and use of the novel change gear unit in relation to other salient and significant parts of a paper cutting machine;

FIG. 2 is a fragmentary diagrammatic view in end elevation of the structure diagrammatically indicated in FIG. 1;

FIG. 3 is a view in side elevation of a novel change gear unit which embodies features of the present invention;

FIG. 4 is a vertical, longitudinal sectional View through the gear box, the section being taken on the line 4-4 of FIG. 5, looking in the direction of the arrows;

FIG. 5 is a view in front elevation of the novel change gear unit;

FIG. 6 is a horizontal sectional view taken on the section line 66 of FIG. 3, looking in the direction of the arrows;

FIG. 7 is an expanded or developed view showing particularly the operative trains which are made selectively available in the novel change gear unit.

In the illustrative mechanism of FIGS. 1 to 7 the web 10 is drawn from a reel (not shown) by a positively driven, positively acting feed couple 15. A flying cutter 18, which is of conventional construction, comprises a stationary blade 22 and a cooperative rotary blade 20, the latter blade being mounted on a cutter drum 146 which is fast on a cutter shaft 148. As is well understood, the web 10 must run at a lower linear speed than the blade 20, but, subject to that limitation, the speed of the web may be adjusted relative to the speed of the cutter in order to select and control the length of sheet consistently cut. The change gear unit 23 (FIGS. 3 to 7) is adapted to select and maintain any one of a large number of gear ratios between its input shaft 160 and its output shaft 178, whereby the length of the sheet cut may be accurately predetermined and maintained by the setting of the unit.

A motor M drives the input shaft 160 of the unit 23, and the shaft 160 drives the cutter operating shaft 148 in fixed linear relation to its own operation. The feed couple 15, on the other hand, is driven through the unit 23, the ultimate output shaft 178 of the unit 23 being connected to drive the feed couple 15 in fixed linear relation to itself.

The change gear unit 23 comprises a casing 150 which is a four story structure consisting essentially of four casing members 152, 154, 156 and 158. Shafts 160 and 162 are rotatably supported between sections 152 and 154; shafts 164 and 166 are rotatably supported between sections 154 and 156; and shafts 168 and 170 are rotatably supported between sections 156 and 158. Also supported at the level of the juncture of sections 154 and 156 is a series of axially aligned shafts 172, 174, 176 and 178. The shafts 172 and 17 8 are received between end walls of the sections 154 and 156. Internal brackets 180 which form integral parts of section 154 provide lower half bearings for the shafts 1'74 and 176. Complementary half bearings 182 are secured upon the brackets 180.

The shaft 160 constitutes a common drive shaft for the flying cutter 18 and for the web drive shaft 178. The shaft 160 is driven from its left end (as viewed in FIGS. 5 and 7), and has its right end connected with the cutter shaft 148 in an output-input ratio of two to one. In other words, the shaft 160 always makes two revolutions for each revolution of the cutter shaft 148.

Each of the shafts 160, 164 and 168 constitutes a denominational input shaft for the change gear unit, the shafts 164 and 168 being themselves constantly driven in fixed ratios from the shaft 160. The shafts 162, 166 and 170 are associated with the respective shafts 160, 164 and 168 and form parts of settable transmission connections to the ultimate output shaft 178. The input component through the shaft 162 is adjusted by increments of five inches per cutter cycle; the input component through the shaft 166 is adjusted by increments of one-half inch per cutter cycle; and the input component through the shaft 170 is adjusted by increments of one-sixteenth inch per cutter cycle.

The illustrative disclosure has been made specific for the purpose of facilitating an understanding of the principle of operation of the unit 23, but it will be recognized, of course, that the invention is not limited to these specific details.

The shaft 166 is connected through gears 184 and 186 to drive the shaft 164 constantly at the rate of one revolution for each four revolutions of the shaft 160. The shaft 164 is similarly connected through gears 188 and 1% to drive the shaft 168 constantly at the rate of one revolution for each four revolutions of the shaft 164, and hence for each sixteen revolutions of the shaft 160.

The shaft 161 has fast upon it a series of gears of different diameters which are adapted to be selectively coupled in driving relation to the shaft 162. The gears from left to right are provided with 30, 35, 40, 45, 50, 55, 60, 65, 70 and 75 teeth, respectively. A yoke 192 embraces, and is rockably mounted upon, gear 196, which gear is splined upon the shaft 162. A coupling pinion 194 which is adapted to be selectively engaged with any one of the coupling gears of the shaft 160 is slidable along the shaft 162, but because of its splined engagement with the shaft, it compels the shaft to rotate in unison with itself.

The yoke 192 has a handle portion 198 which extends through a sloping slot 201) in a front cover plate 2112. The upper edge of the slot 2110 is formed with index notches 261 for receiving the upper margin of the handle 188. Opposite each notch there is an index numeral showing in inches the feed component of the web per cutter cycle which results from the setting of the handle in the associated notch.

A knurled operating head 284 on the handle 198 may be used for unlocking the handle 198, shifting the handle lengthwise of the shaft 162, and relocking the handle. The head 204 forms part of a spring plunger (not fully illustrated in detail) which includes an integral latching pin 296. The pin 296, for any setting of the change gear unit, will occupy one or another of a series of latching holes 208 (one for each of the notches 201). When it is desired to change the setting, the head 284 is pulled forward to free the pin 286 from the latching hole 201 which it occupies, the handle is then swung downward as far as possible for engagement with the straight lower edge of the slot 268, and is shifted along the slot and then rocked upward into the desired notch 201. The head 284 is then allowed to shift under spring impulsion in a direction to carry the pin 266 into the hole 208 associated with the selected notch.

Rotation of the shaft 162 is transmitted through output gear 210 to a compound gear 212, 214, which is mounted on the shaft 169 with freedom for rotation relative thereto. The gear 214 drives an equal gear 216, the latter gear being supported on the shaft 172 with freedom for rotation relative to the shaft. The gear 216 is fast with an input side gear 218 of a bevel gear differential 220.

Rotation of the gear 218 in one direction will then produce equal rotation of the other input side differential gear 224 and the shaft 174 in the opposite direction.

The shaft 174 positively drives the shaft 176 in unison with itself at all times. The shaft 176 has fast upon it an input side gear 226 of a second bevel gear differential 228. The input of the gear 226 is transmitted through spider gears 238 and a spider 232 upon which they are carried, to the ultimate output shaft 178, the spider being made fast upon the shaft 178. Rotation of the gear 226 causes rotation of the shaft 178 in the same direction as itself, but at one-half its own rotary speed.

Since the number of teeth is indicated on the drawing for each gear of the described train (other than the bevel gears of the differentials), it is a simple matter to determine that the effect of setting the pinion 194 in mesh with the 45 toothed gear on the shaft 168, will be that for two revolutions of the shaft 166, or one cutting cycle, a web feed component of 45 inches will be produced. This may readily be generalized to the statement that for any setting involving a gear of 11 teeth on the shaft 160, the corresponding web feed component produced by that setting is 11 inches per cutter cycle. The total feed, of course, is the sum of the components supplied through shafts 162, 166 and 170.

The drives from the shafts 16- and 168 to the shaft 178 are similar in principle to the corresponding drive from the shaft 160 to the shaft 178 which has just been described, and the manner of setting up the connections is also similar.

The shaft 164 has fast upon it a series of gears of different diameters which are adapted to be selectively coupled in driving relation to the shaft 166. The gears from left to right are provided with 10, 20, 30, 40, 50, 60, 70, S and 90 teeth, respectively. A yoke 236, similar to the yoke 192, embraces, and is rotatably mounted upon, the hub portion of a gear 238. The gear 238 is splined on the shaft 166 and is constantly in mesh with a coupling pinion 240. The pinion 248 is rotatively carried by the yoke 236 and is adapted to be coupled selectively with any one of the gears on the shaft 164. The yoke 236, like the yoke 192, has a handle portion equipped with a knurled plunger head 242. The plate 244 is formed with a sloping slot 246 having notches 248, and latching holes 254, the latter for receiving a latch pin 252 which forms an integral part of the plunger head 242.

Any selected gear on the shaft 164 is adapted to fur- 4 nish a characteristic component of Web feed per cutter cycle. These components vary from one-half inch to four and one-half inches, being separated by one-half inch increments.

There is one important difference between the train involving shafts 164 and 166 on the one hand, and the train involving shafts and 162 on the other. One or another of the selectable gears on the shaft 160 is always active, but there will be occasions when no component is wanted from the shaft 164. In the extreme lefthand position of the yoke 236, a stationary gear segment 254 is provided for engagement by the pinion 240, to lock the pinion 240 and the output train therefrom against operation.

The shaft 166 has fast upon it an output gear 256 which drives a gear 258 of a compound gear 258, 260. The gear 260 drives a gear 262 fast on the shaft 172. The shaft 172 has fast upon it the spider 222 of a differential gear 220, whereby the spider gears are carried. The remainder of the connection to the ultimate output shaft 178 has already been described.

Analysis of the complete transmission train from shaft 168 through shafts 164 and 166 to shaft 178 when the 50 tooth gear on the shaft 164 is active, makes it clear that two revolutions of shaft 160, corresponding to one cutter cycle, produces through this train a web feed component of 2.5 inches. If we take 11 as the number of teeth on the selected or active gear of shaft 164, it is readily apparent that n/20 is equal to the number of inches of web feed per cutter cycle for which the train through shaft 164 is responsible. The cover plate 244 is marked accordingly.

The shaft 168 also has fast upon it a series of gears of different diameters which are adapted to be selectively coupled in driving relation to the shaft 170. The gears from left to right are provided with 16, 32, 48, 64, 80, 96 and 112 teeth, respectively. The organization is the same in principle as that of the two denominational trains which have been previously described, except that, for securing output in the desired direction of rotation, two pinions instead of one, are interposed between the active gear on the shaft 168 and the gear 266. A yoke 264 is rockably mounted on the hub portions of a splined gear 266, and embraces the gear. Two meshing pinions 268 and 269 are carried by the yoke, the latter being constantly in mesh with the gear 266. The pinion 268 is adapted to be set into mesh with any one of the transmission gears on the shaft 168. It may also be set into engagement with a stationary gear segment 270 when it is desired to lock the shaft 170 against rotation.

A yoke 264 includes a handle 272, a plunger head 274 and a latch pin 276 which is integral with the plunger head. The handle extends through a slot 278 in a cover plate 284 and is adapted to be located in notches 282 and latched in place by the use of latch holes 284 for detaining the pin 27 6.

The shaft 170 has fast upon it an output gear 286 through which it drives a gear 288 of a compound gear 288, 290, the compound gear being mounted on the shaft 168 with freedom for rotation relative thereto. The gear 290 drives a gear 292 which is revolubly mounted on the ultimate output shaft 178, but is secured in fixed relation to the side input gear 234 of the differential 228.

Analysis of the complete transmission train from the shaft 166 through shafts 168 and 170 to the shaft 178, when the 32 tooth gear on the shaft 168 is active, reveals that two revolutions of 160, corresponding to one cutter cycle, produces through this train one-eighth inch of Web feed. If we take 12 as the number of teeth on the selected or active gear of shaft 168, it is readily apparent that n"/ 25 6 is equal to the number of inches of Web feed per cutter cycle for which the train through shaft 168 is responsible. The cover plate 280 is marked accordingly.

It will now be clear that through the many available inputs and combinations of inputs, the positive change gear unit can be set to cause sheets to be cut at one-sixteenth inch intervals throughout the entire range from thirty inches to 79 inches.

Obviously, the unit 23 could be redesigned without departure from the principles outlined above to operate between other limiting ratios than those stated and with the relative weights of the several denominational input shafts changed. The constant increment between available inputoutput ratios, could, of course, be changed also.

It will be particularly noted that the illustrative gear unit 23 is characterized by the combination of the following features:

(1) A series of denominational input shafts disposed in a common vertical plane and equally spaced apart, are constantly operatively connected to one another through fixed ratio positive gearing, so that one may be a common driver and each will have a definitely assigned, fixed weight relative to the others;

(2) A series of coupling shafts equal in number to the number of denominational input shafts, the coupling shafts being mounted in a common vertical plane which-is located in front of the common veritcal plane, of the denominational input shafts, each coupling shaft being operatively asosciated with one of the denominational input shafts and located at the same level therewith;

(3) A series of gears of graduated sizes fixed on each denominational input shaft and settable couple gearing carried on each coupling shaft for effecting operative connection with any selected one of the graduated gears on the associated denominational input shaft and thereby transmitting motion to the coupling shaft;

(4) An output assembly consisting of a plurality of denominational gears and input and output shafts therefor including an ultimate output shaft, all mounted for operation about a common axis Which-is located behind the denomination input shafts and substantially in line with associated intermediate denominational input and coupling shafts;

(5) Gear trains from the coupling shafts to the appropriate denominational input shafts consisting in each instance of fixed gears on the associated coupling and differential input shafts, and intermediate compound idler gears on the associated denominational input shaft, the output assembly being constructed and arranged to combine and transmit all the denominational output components as a single composite output to the ultimate output shaft;

(6) A casing composed of sections built up and secured to one another in a tiered, or storied formation, the abutting boundary portions in each pair of adjacent sections including complementary bearing members for rotatably supporting opposite ends of one of the denominational input shafts and its associated coupling shaft, and the abutting boundary portions of an intermediate pair of adjacent sections including complementary bearing supports for the output assembly; and

(7) Each settable coupling gearing including a handle lever which extends rearward from the coupling shaft on which it is carried into proximity with the associated denominational input shaft, and forward from the coupling shaft through the forward wall of the casing.

While a preferred embodiments of the invention has been illustrated and described in detail, it is to be understood that changes may be made therein and the invention embodied in other structures. It is not, therefore, the intention to limit the patent to the specific construction illustrated, but to cover the invention broadly in whatever form its principle may be utilized.

I claim:

1. A plural denomination, positive change gear unit comprising (a) first, second, and third denominational input shafts equally spaced apart in the same vertical plane, (b) gears fixed on said input shafts drivingly connecting each of said shafts to at least one of the others so that one of said input shafts may serve as the common driver for all of said shafts,

(c) first, second, and third coupling shafts equally spaced apart in the same vertical plane which is parallel to the vertical plane of the denominational input shafts, each of said coupling shafts lying in a horizontal plane common to one of the denominational input shafts and operatively associated therewith,

(d) an output assembly including a pair of differential gear units each having a pair of inputs, a pair of spider gears, and a spider, a first input of one of said pair of differentials being directly connected to an input of the other of said pair of differentials, said output assembly further including an input shaft attached to the spider of said one differential and an ultimate output shaft attached to the spider of said other differential, said input and output shafts for said differentials in axial alignment in the horizontal plane of the second denominational input shaft and the second coupling shaft,

(e) a plurality of gears of graduated sizes fast on each denominational input shaft,

(f) settable coupling gearing carried on each coupling shaft drivingly connecting each coupling shaft with any selected one of the graduated gears on the associated denominational input shaft,

(g) an output gear fixed on each coupling shaft,

(h) idler bearing carried on each denominational input shaft and meshing with said output gear on the associated coupling shaft,

(i) said idler gearing on the first denominational input shaft drivingly connecting said first coupling shaft to a second input of said one differential,

(j) said'idler gearing on the second denominational input shaft drivingly connecting said second coupling shaft to the spider of said one differential to turn the spider and thereby add to the output from said one differential, the resultant output from said one differential being transmitted to said other differential by the direct connection between the first input of said one differential and an input of said other differential,

(k) said idler gearing on the third denominational input shaft drivingly connecting said third coupling shaft to an input of said other differential to add to the ultimate output from said other differential.

2. A plural denomination, positive change gear unit in combination with a web cutting mechanism, comprising (a) first, second, and third denominational inputshafts equally spaced apart in the same vertical plane,

(b) gears fixed on said input shafts drivingly connecting each of said shafts to at least one of the others so that one of said input shafts may serve as the common driver for all of said shafts,

(c) first, second, and third coupling shafts equally spaced apart in the same vertical plane which is parallel to the vertical plane of the denominational input shafts, each of said coupling shafts lying in a horizontal plane common to one of the denominational input shafts and operatively associated therewith,

(d) an output assembly including a pair of differential gear units each having a pair of inputs, a pair of spider gears, and a spider, a first input of one of said pair of differentials being directly connected to an input of the other of said pair of differentials, said output assembly further including an input shaft attached to the spider of said one differential and an ultimate output shaft attached to the spider of said other differential, said input and output shafts for said differentials in axial alignment in the horizontal plane of the second denominational input shaft and the second coupling shaft and parallel to the second denominational input shaft,

(e) positively gripping web feed rolls for feeding web (j) settable coupling gearing carried on each coupling material to a web cutter, shaft drivingly connecting each coupling shaft with (1) means drivingly connecting the feed rolls with the any selected one of the graduated gears on the assoultirnate output shaft for positive operation with the ciated denominational input shaft, said first coupling ultimate output shaft, shaft being connected by said coupling gearing to a (g) a flying cutter for severing sheets from the leading graduated gear of n teeth on said first denominational end of the web material, input shaft, the second coupling shaft being con- (h) means drivingly connecting a rotary cutter drum nected by said coupling gears to a graduated gear of of the flying cutter with the first denominational inn teeth on said second denominational input shaft, put shaft for positive operation with said input shaft, 10 th third coupling haft being c nnected by said a plu y of gears of graduated Sizes fast On each coupling gearing to a graduated gear of n" teeth on denominational input shaft, said third denominational input shaft,

(j) settable coupling gearing carried on each coupling (k) an output gear fixed on each coupling shaft,

Shaft drivingly Cohhficlhlg each Coupling Shaft With (l) idler gearing carried by each denominational input any selected one of the graduated gears on the assohaft and meshing ith aid out ut gear on the associated denominational input shaft, ciated coupling shaft,

( an Output g fixed n each p g shaft, (m) said idler gearing on the first denominational input idler gearing carried on fiach denominational input shaft drivingly connecting said first coupling shaft Shaft and meshing with Said Output ghaf 011 the 3550' to a second input of said one differential to yield an ciated Coupling Shaft, output from said one differential which corresponds said idler gearing On the first denominational ihPht to a web feed component of 12 inches from said web shaft drivingly connecting said first coupling shaft f d 11 t0 a Second input of Said 0116 difiefemial, (n) said idler gearing on the second denominational Said idler gearing 011 the Second denommahohhl input shaft drivingly connecting said second coupling input Shaft drivingly whhfictihg Said Second Coupling shaft to the spider of said one differential to turn shaft to the spider of said one differential to turn the spider and thereby add to the output from said one differential, the resultant output from said one differential being transmitted to said other differential by the direct connection between the first input of said one differential and an input of said other difsaid spider and thereby add to the output from said one differential an amount which corresponds to a web feed component from said web feed rolls of n'/20 inches to yield a combined output from said one differential which corresponds to a web feed component of ferential,

(0) said idler gearing on the third denominational input shaft drivingly connecting said third coupling shaft to an input of said other differential to add to the ultimate output from said other differential.

3. A plural denomination, positive change gear unit in combination with a web cutting mechanism, comprising (a) first, second, and third denominational input shafts equally spaced apart in the same vertical plane, 40

(b) gears fixed on said input shafts drivingly connecting each of said shafts to at least one of the others so that one of said input shafts may serve as the common driver for all of said shafts,

(c) first, second, and third coupling shafts equally inches, said combined output from said one differential being transmitted to said other differential by the direct connection between the first input of said one differential and an input of said other differential,

(0) said idler gearing on said third denominational input shaft drivingly connecting said third coupling shaft to an input of said other differential to add to the ultimate output from said other differential an amount which corresponds to a web feed component from said web feed rolls of n/256 inches to yield spaced apart in the same vertical plane which is 45,

parallel to the vertical plane of the denominational input shafts, each of said coupling shafts lying in a a combined ultimate output from said other differential which corresponds to a web feed component of horizontal plane common to one of the denominational input shafts and operatively associated therewith, t

(d) an output assembly including a pair of differential gear units each having a pair of inputs, a pair of sp lder gears, a mput of one of 4. The combination set forth in claim 3 Where It varies sa1d Pa1r of dlfierennals i cqnnecteii to from 30 to 75 in increments of five to yield web feed of the other of f of dlfferenuals components in five inch increments, It varies from 10 said Output assembly further mcludmg an mplft Shaft to 90 increments of ten to yield web feed components attache d t0 the spider of Said one difierentlal and in one-half inch increments, and n" varies from 16 to ummate F f to the Splder of 112 in increments of sixteen to yield web feed components Sald and shafl s in one-sixteenth inch increments, the web feed comfor Said dlfierentlals axlal ahgnmnt the ponents being added to provide an ultimate Web feed zontal plane of the second denominational input component in the range of from 30 to 791%6 inches from shaft and the second coupling shaft, the Web feed m11s (e) positively gripping Web feed rolls for feeding web material to a web cutter,

(1) means drivingly connecting the feed rolls with the ultimate output shaft for positive operation with inches.

References Cited in the file of this patent UNITED STATES PATENTS the ultimate output shaft, 601,200 Meisel Mar. 22, 1898 (g) a flying cutter for severing sheets from the leading 1,852,282 Biggert Apr. 5, 1932 end of the web material, 1,967,559 Schreck July 24, 1934 (It) means drivingly connecting a rotary cutter drum 2,070,537 Mathews Feb. 9, 1937 of the flying cutter with the first denominational 2,131,531 Behrens Sept. 27, 1938 input shaft for positive operation with said input 2,521,771 Bechle Sept. 12, 1950 shaft, 2,789,445 Kaufmann et al. Apr. 23, 1957 (i) a plurality of gears of graduated sizes fast on 2,804,784 Blumentritt Sept. 3, 1957 each denominational input shaft, 3,060,766 Heinrich Oct. 30, 1962 

2. A PLURAL DENOMINATION, POSITIVE CHANGE GEAR UNIT IN COMBINATION WITH A WEB CUTTING MECHANISM, COMPRISING (A) FIRST, SECOND, AND THIRD DENOMINATIONAL INPUT SHAFTS EQUALLY SPACED APART IN THE SAME VERTICAL PLANE, (B) GEARS FIXED ON SAID INPUT SHAFTS DRIVINGLY CONNECTING EACH OF SAID SHAFTS TO AT LEAST ONE OF THE OTHERS SO THAT ONE OF SAID INPUT SHAFTS MAY SERVE AS THE COMMON DRIVER FOR ALL OF SAID SHAFTS, (C) FIRST, SECOND, AND THIRD COUPLING SHAFTS EQUALLY SPACED APART IN THE SAME VERTICAL PLANE WHICH IS PARALLEL TO THE VERTICAL PLANE OF THE DENOMINATIONAL INPUT SHAFTS, EACH OF SAID COUPLING SHAFTS LYING IN A HORIZONTAL PLANE COMMON TO ONE OF THE DENOMINATIONAL INPUT SHAFTS AND OPERATIVELY ASSOCIATED THEREWITH, (D) AN OUTPUT ASSEMBLY INCLUDING A PAIR OF DIFFERENTIAL GEAR UNITS EACH HAVING A PAIR OF INPUTS, A PAIR OF SPIDER GEARS, AND A SPIDER, A FIRST INPUT OF ONE OF SAID PAIR OF DIFFERENTIALS BEING DIRECTLY CONNECTED TO AN INPUT OF THE OTHER OF SAID PAIR OF DIFFERENTIALS, SAID OUTPUT ASSEMBLY FURTHER INCLUDING AN INPUT SHAFT ATTACHED TO THE SPIDER OF SAID ONE DIFFERENTIAL AND AN ULTIMATE OUTPUT SHAFT ATTACHED TO THE SPIDER OF SAID OTHER DIFFERENTIAL, SAID INPUT AND OUTPUT SHAFTS FOR SAID DIFFERENTIALS IN AXIAL ALIGNMENT IN THE HORIZONTAL PLANE OF THE SECOND DENOMINATIONAL INPUT SHAFT AND THE SECOND COUPLING SHAFT AND PARALLEL TO THE SECOND DENOMINATIONAL INPUT SHAFT, (E) POSITIVELY GRIPPING WEB FEED ROLLS FOR FEEDING WEB MATERIAL TO A WEB CUTTER, (F) MEANS DRIVINGLY CONNECTING THE FEED ROLLS WITH THE ULTIMATE OUTPUT SHAFT FOR POSITIVE OPERATION WITH THE ULTIMATE OUTPUT SHAFT, 